Fluid proportioning system



Nov. 13, 1945. T. A. BAKER FLUID PROPORTIONING SYSTEM original "Filed May 12, 1942 IN V EN TOR.

www EN wml Patented Nov. 13, 1945 FLUID PROPORTIONING SYS Thomas A. Baker, Logansport, lud.

Original application May l2, 1942,' Serial No.

442,711. Divided and this application Becomber 24, 1942, Serial No. 470,016

lil Claims.

My invention relates in general to fluid measuring system and more particularly to air and liquid measuring system wherein the quantity of liquid and the quantity of air may be separately determined and wherein the ratio of air delivery to liquid delivery may be varied to meet certain requirements.

Although my invention will be described yin connection with the supplying of a measured quantity of liquid fuel and a measured quantity of air to an internal combustion engine, yet it is to be understood that my invention is adaptable' to other uses. l

An object oi my invention is the provision of measuring the quantity o liquid delivered through a iiow duct passage. I V

Another object of my invention is the provision ci measuring the quantity of air which ows through an air duct passage.

Another object of my invention is the provision of measuring the quantity of air passing through an air duct passage wherein the provision compensates for the density of the air owing through the air duct passages.

Another object oi my invention is the provision of compensating for changes in the density ci the air while measuring the quantity of the flow of air through an air duct passage.

Another object of my invention is the provision of maintaining the quantity of the iiow of air in an air duct passage at a predetermined value or setting, wherein the predetermined value or setting is compensated for changes inthe density of the air. ,c

Another object of my invention is the provision of controlling the amount of the flow of air through an air duct passage while automatically compensating for variable changes in the density of the air.

Another object of my invention is the provision of compensating for variable changes in the tern--v perature, in the humidity, and in the absolute pressure of the air passing through an air duct passage while controlling and determining the quantity of the ilow of air through the air duct passage.

Another object of my invention is the provision of a metering pump device capable of measuring the liquid fuel in a predetermined quantity as determined by pressure condition of the ow of the fluid and of causing the time discharge of the measured liquid fuel to the nozzle valve of the internal combustion engine at the proper interval.

Another object of my invention is the provision (Cl. img-139) of transmitting the movement oi an air weighing apparatus to a control vane or other control device in an air duct passage, whereby the quantity of the flow of air through the air duct passage may be maintained at a predetermined value or setting.

Another object of my invention is the provision of measuring the quantity of liquid which ows through a liquid duct passage and oi' maintaining the ow of liquid through the liquid duct passage at a predetermined value or setting.

Another object of my invention is the provision of using the pressure oi the liquid flowing in the liquid duct passages for operating the motion transmitting means between the liquid measuring device and the control means which governs the amount of liquid nowing through theair duct paratus and the control vanes which govern the now of air through the air duct passage.

Another object of my invention is the provision of supplying both air and liquid fuel to an in-x ternal combustion engine and oi varying the ratio of the quantity of air to thequantity of liquid fuel delivered to the engine.

Another object oi my invention is the provision of a liquid pump, wherein the volume delivery of the pump may he varied by changing the stroke of a plurality of radially extending pistons by a suitable eccentric and variably adjustable cranl; head.

Another object of my invention is the provision of a uid pressure follower apparatus arranged to control the flow of the air passing through an air duct passage or the liquid through a liquid duct passage in which the fluid pressure follower apparatus is governed by a pilot piston.

Other objects and a fuller understanding of my invention may be had by referring to the following description and claims, taken in conjunction with the accompanying drawing, in which like parts are designated by like reference characters and, in which:

The ligure represents a diagrammatic illustration of a system for supplying both air and liquid 'to an internal combustion engine 'wherein the quantity of air and the quantity of the liquid are both measured and wherein the ratio of the delivery of the air to the delivery of the liquid may be adjustably varied with reference to each other.

With reference to the drawing, which shows the diagrammati illustration of my invention, I illustrate my ir control apparatus supplying air to the cylinder 33 of an internal combustion engine and my fuel control apparatus for supplying fuel to the cylinder 33 of the internal combustion engine. The controlled air is supplied to the cylinder 33 through a conduit 30 and a branch conduit 3|. In the drawing only one cylinder of the internal combustion engine is illustrated and it is to be understood that the air duct leads to the other cylinders 'of the engine. Any suitable means for establishing air under pressure may be employed to supply the air duct 30. The fuel to the cylinder 33 is supplied through a fuel pipe 54 and is controlled by an illustrated valve 55 mounted on top of the cylinder 33.

In my invention the air which is supplied to the cylinder 33 is measured in terms of the quantity of air whichis passing a given point in a given period of time. The mechanism for weighing or measuring the air passing through the air duct 30 is indicated generally by the referencev character 35. The resultant movement of the air weighing mechanism 35 is transmitted through a shaft |24 to a motion transmitting means indicated generally by the reference character 36 which controls the position of the control vane 31 in the air duct 30. The motion transmitting means 36 is governed by a throttle device indicated generally by the reference character 38 which adjustably varies the amount of air passing through the air duct 30 to the internal combustion engine. Accordingly, through the combined action of the air measuring mechanism 35 and the motion transmitting means 36, the quantity of air passing through the air duct 30 may be maintained at a deiinite predetermined value or setting as regulated by the throttle device 38.

The fuel which is delivered to the internal combustion engine 33 through the supply conduit 54 is fed by a. pump 56 from a supply tank 206. The fuel upon leaving the pump passes through a venturi 260 and then into a liquid metering or measuring device indicated generally by the reference character 53, after which the measured liquid is supplied to the cylinder 33 through a supply duct 54. Although nonly one outlet 54' is illustrated for the liquid metering device it is to be understood that the liquid metering device has as many outlets as there are cylinders in the engine to be supplied. The liquid metering device 53 and the pump 56 may be driven by a common source of motive power indicated generally by the reference character iM. The liquid metering device 53 is capable of having a variable volume delivery which governs the flow of the amount of iiuid to the cylinders of the internal combustion engine. The variable volume delivery of the liquid metering device is controlled by a motion transmitting means 228 which in turn is responsive to two opposing pressure bellows and |48, each being yrespectively responsive to the low and high pressure condition at the venturi 260. The motion transmitting means 228 is governed by the throttle device 38 as indicated by the dotted line 221 which may comprise a flexible shaft for driving the gear 224. Consequently, the combined action of the liquid metering device 53 and the motion transmitting means 228 provide for maintaining the flow of fluid to the cylinder 33 of a predetermined value or quantity as governed by the setting of the throttle 38. 'I'he combined action of my air control mechanism and of my iiuid control mechanism as governed by the throttle 38 is such that the proper amount of air and the proper amount of fuel is delivered to the cylinder of the internal combustion engine to give high efficient results. The throttle device 38 is provided with two dualcontrol levers indicated by the reference characters 228 and 232, the control lever 232 being the throttle lever and the lever 229 being the ratio mixing lever which varies the ratio of air supplied to the cylinder with reference to the amount of fuel supplied to the cylinder.

My fluid flow responsive mechanism 35 comprises generally a variable gearing compartment indicated by the reference character 39 and a density factor compartment indicated by the reference character 40 and a velocity pressure unii-l indicated generally by the reference character 4|. The density factor compartment 40 is arranged to receive a, continual sampling o the air from the air duct 30. The continuous sampling of the air from the air duct 30 is supplied through the density factor compartment 40 through a duct and is returned back to the air duct 30 through an air passage 88. The air is continually circulated through the density factor compartment 40 by reason of the fact that the air duct 95 is responsive to the total pressure of the air in the air duct 30 whereas the air duct 98 is responsive to the static pressure of the air in the air duct 30, thereby producing a differential pressure which forces the air continually through the density factor compartment. In the top of the density factor compartment 40 is mounted a temperature responsive bellows |25. in the middle of the compartment is mounted a moisture responsive device |39 and in the bottom of thecompartment is mounted an absolute' pressure responsive device 86. These three responsive devices give a movement or measurment which is a function of the density of the air by-passed through the density factor compartment 40 from theair supply duct 30 to the in' terna] combustion engine. In other words, in my fluid flow responsive device I compensate for changes in the density of the air so that a true measurement or movement is given which corresponds to the actual quantity or weight of air passing through the duct 30. The temperature responsive bellows |25 may be suitably anchored to the side wall 0f the density factor compartment 4U. As ythe temperature of the air in the compartment increases the bellows actuate the shaft |21 to the left. The moisture responsive device |39 comprises a plurality of moisture responsive elements |4| so that as the moisture responsive elements |4| change their elongation the shaft |40 is moved in a transverse direction. 'I'he moisture responsive elements |4| may be made of any suitable material and I find that human hair is of the nature to give satisfactory results although the moisture responsive elements are not limited to the employment of hair but include any other material. Also, it is to be understood that the moisture responsive device |38 may be of a form entirely different from that shown in the drawing which is but one embodiment of several types of moisture responsive devices. As the sampling of the air which passes through the density factor compartment 40 increases in moisture content, the shaft |40 moves to the right as shown in the drawing. The absolute pressure responsive device 88 comprises generally a kbellows 88 and the movement of the bellows 88 is responsive to the absolute pressure aaaaeea of the air passing through the density factor compartment 40. As the absolute pressure increases, the shaft 93 moves to the right as shown in the drawing.

I ity pressure of the air as it passes through a conduit. In vmy invention the density of the air is compensated for by the combined action of the temperature responsive device |25, the moisture responsive device |39, and the absolute pressure device 06. The velocity pressure of the air is measured or determined by the velocity pressure unit 4| which is connected to the air conduit 30 through a tube 44 which is responsive to the total pressure of the air within the air conduit 30 and through a tube 45 which is responsive to the static pressure of the air in the air conduit 30.-

The differential between the total pressure and the static pressure represents the'velocity'pressure of the air in the conduit and accordingly the movement bf the shaft 66 is responsive to the velocity pressure of the air in the conduit 30. An increase in the velocity'pressure of the air tends to rotate the shaft 66 in a counterclockwise direction as shown by the arrow in the drawing. The shaft 66 actuates a variable rotor drive means 15 through means of a radially disposed pln 19, which engages an angularly disposed slot 80 in the wall of the variableV rotor drive means 15 which comprises a cylindrical housing or drive member surrounding the shafts 66 and 93. The drive shaft 66 and the cylindrical housing or drive member are axially movable relative to each other, whereby the slidable movement of thepin 19 in the slot 80 varies the angular relationship between the drive shaft and the cylindrical housing or drive member. Actuation of the shaft 93 by the absolute pressure responsive device 06 causes the pin 19 to be moved within the angularly disposed slot 80, with the result that the movement of the shaft 93 provides for causing the gear 83 to be compensated for changes in the absolute pressure. In other words, .the movement of the gear 83 ls responsive to the velocity pressure device 4| as modified by the movement of the absolute pressure responsive device 86. The movement of the gear 63 is transmitted to a gear |04 which in turn drives a variable rotor drive means 10B-through the arrangement of a pin and slot as illustrated. The variable rotor drive means |06 drives the gear |01 but the transmission of motion from the variable rotor drive means |06-to the gear |01 I is modified by the movements of the shaft |40 which is actuated by the humidity device |39. In other words, the movement of the gear |01 is compensated for by reason of changes in the humidity. The movement ofthe gear |01 is transmltted to a gear |08 which in .turn transmits movement to a variable rotor drive means ||4 through the pin and slot arrangement as illustrated. The movement of the variable rotor drive means ||4 is transmitted to the gear |23 but the transmission of movement is modified by the actuation of the shaft |21 which ls connected to the temperature responsive device |25. That is to say, the movement of the variable rotor drive means |I4 to the gear |23 is compensated for by changes in the temperature. 'I'he construction of the fluid responsive device 35 with its comvelocity pressure device lli may be the same as that shown and described in my parent application Serial No. 442,711 filed May 12, 1942, for Fluidmeasurlng and regulating mechanism, and in my divisional patent application Serial No. 459,410 filed September 23, 1942, for Fluid flow responsive device.

The shaft |20 may be characterized as a resultant output shaft because it is responsive to the movement of the velocity pressure unit 0| as modif-led by the temperature responsive unit E25, the moisture responsive unit |30 and the absolute pressure responsive unit 00. In other words, the resultant output shaft d20 produces a movement which is a measurement of the weight of the air or the quantity of the air in the duct 30 passing a given point in a givenperiod of time. Thus the resultant output shaft 20 is'a function of the velocity pressure and the density as measured by the combined action of the temperature responsive device 125, the moisture responsive device |39vand the absolute pressure responsive device 86. The movement of the shaft H20 is arranged to govern the position of the control vane '31 within the conduit 30 through the motion transmitting means indicated by the reference character 36 in the figure of the drawing.

The motion transmitting means may be of the same construction as that shown and described in my parent -application Serial No. 442,711 flied May 12, 1942, for Fluid measuring and regulating mechanism and comprises generally a master valve |51, a slidable and rotatable plunger |159 and a rotatable casing |56 which govern the flow of fluid to a pilot piston |96 that actuates a fluid follower mechanism |88 having a followerplunger |90 for actuating the vane 31. In operation., the setting of the master valve |51 is eected by rotating the rotatable casing |50 through means of a gear 201 actuated by the throttle 38 through a mechanical movement 201 which may comprise a flexible shaft. The slidable and rotatable plunger |59 of the master valve |51 is actuated by the shaft |20. The master valve |51 controls the position of the fluid follower plunger |90 by governing the flow of the fluid which is admitted to opposite sides of the pilot piston |96. Fluid is admitted under pressure from the pump 56 through the fluid inlet duct |89 to the master valve |51,`and through control ports within the master valve 51 fluid is admitted to or exhausted from the pilot cylinder |91 through the fluid ducts 202 and 203. Fluid to the follower plunger |90 is admitted through a fluid duct |98 and the operation is such that the follower plunger |90 follows the movements of the pilot piston |96. The exhaust fluid ilows through the fluid duct 200 to the supply reservoir 206. When the master valve is in its neutral or normal position,

the two engaging discs of the clutch |18 hold the pilot piston |96 in a fixed position through the shaft |19, the pinion gear |80, and the rack teeth |8| with the result that the control vane 31 within the airy duct 30 is maintained in a fixed ponent parts; namely, the variable gearing compartment 39, the uid density device 40, and the to cause lthe quantity of the'air to be maintained at a predetermined value or setting as determined by the throttle device 38. The effect produced by rotating the rotatable casing |58 is such as to change the setting of the master valve |51 to produce a corresponding re-positioning of the control vane 31. Y

The re-positioning of the rotatable casing |58 is effected by moving the throttle lever 232 which actuates a gear segment 209 that engages the bevel gear 208 connected to the exible drive shaft 201. The gear segment 209 is keyed or secured to a hub 2 I8. I'he throttle lever 232 may be moved to any one of many adjustable positions. In operating the flexible shaft 201 for turning the gear |1| for rotating the rotatable casing |58, it is only necessary for the operator to move the throttle lever 232 to any desired operating position. The actuation of the throttle lever 232 also rotates the rotor 2|4 which rotates the bevel gear 2|2 through a gear segment 2|3. The rotation of the bevel gear 2|2 operates the exible shaft 221 which turns the gear wheel 224 for governing the motion transmitting means 228 that varies the operation of the liquid metering device 53. The change in the rotation of the gear 224 through the motion transmitting means 228 varies the amount of liquid delivered from the liquid metering device 53 to the cylinders of the internal combustion engine. The ratio between the amount of air and the amount of liquid fuel supplied to the internal combustion engine is regulated by the ratio mixing lever 229 of the throttle device 38. A movement of the ratio mixing lever 229 operates a shaft 230 which carries at the right-hand end thereof two cross-pins 223 which engage angular slots 222 in the rotor 2|4. The shaft 230 is provided with a sliding key connection 2|6 which enables the shaft 230 to be axially movable with reference to the hub 2|8 but which rotates with the hub when the throttle lever 232 `is moved. 'I he rotor 2|4 is supported externally by ball bearings 2|5 and internally about ball bearings 22|. The arrangement of the rotor 2|4 and the two cross-pins 223 fitting in the angular slot 222 is of substantially the same construction as the variable rotor drive means 15, |06 and ||4 of the air measuring mechanism 35 shown and described in my parent application No. 442311,.

filed May 12, 1942 for Fluid measuring and regulating mechanism and in my divisional application, Serial No. 459,410, led September 23, 1942, for Fluid flow responsive device. The ratio mixing lever 229 is arranged to be held in any one .of a number of adjustable positions by making engagement with a semi-circular ratchet member 23|. In operation, the ratio mixing lever 229 is actuated to produce the most efllcient operation of the internal combustion engine by varying the ratio between the air supplied to the internal combustion engine and the fuel supplied to the internal combustion engine.

The liquid metering device 53 ls substantially tne same as that shown and described in my parent application No. 442,711, filed May 12, 1942, for Fluid measuring and regulating device, and my divisional application, Serial No. 470,015, filed December 24, 1942, for Liquid metering device, and comprises a housing 26|V which is supplied by liquid fuel from the pump 56 through a feed pipe 259. Within the housing 26| there are arranged a plurality of annularly positioned cylinders indicated generally by the reference character 262. In the embodiment shown in the drawlng there are eight of such annularly arranged assaeeo cylinders 262. The cylinders v262 are formed by cylindrical sleeves 263 fitting into the housing 26|.

Within the cylindrical sleeves 26,3, I provide valvelike pistons 264 which govern the amount of fluid delivered to the internal combustion engine throughthe conduit 54. The valve-like piston 264 comprises a valve 255 having a stem 266 and a valve sleeve 261 on the outside of the valve stem 266. Each of the valve sleeves 261 is provided with a longitudinal duct not shown to direct fuel into the'left-hand end of the cylinders 262. In addition, fluid may flow into the cylinder 262 through longitudinal ducts 269 passing through the internal body part of the liquid metering device. The fluid which flows through the longitudinal ducts 269 is required to pass by ball check valves 210 before entering the cylinders 262. The fluid which is ejected from the cylinders 262 upon the valve-like piston 264 moving to the left is ejected by the ball check valve 21| before entering the conduit 54 to the cylinder of the internal combustion engine.

The. valve sleeve 261 extends to the right and is provided upon its right-hand end with a socket 215 which receives an actuating member 216 operated by a wheel 214 by a rotating plate 219. The wheels 214 are constrained against the rotating plate by means of springs 211 positioned inside of the actuating members 216. The rotating plate 219 is provided with a circular race-way 216 having a raised portion .or cam `260 which when the wheel 214 rides thereover actuates the actuating member 216 to the left. When the left-hand end of the actuating member 216 engages the bottom of the socket 215, the movement of the wheel 214 is transmitted to the valve sleeve 261, preparatory to ejecting the fluid from the cylinders 262. The rotating plate 219 is driven by a drive shaft 26| which may be rotated by any suitable motive power means as indicated by the reference character |0|. i

The valve stems 266 are controlled by a positionable plate 281 engaging the caps 291 which rest upon the right-hand ends of the valve stems 266. The caps 291 are anchored to the valve stems 266 and springs 292 are arranged to bias the valvestems 266 to the right. The positionable plate 281 is connected to a follower plunger |90 by means of a shaft 269. Springs 290 are provided to urge the valve sleeves 261 to the right. The position of the positionable plate 281 is governed by the follower plunger |90 which in turn is controlled by a pilot plunger |85. The pilot plunger is governed by a pilot piston 302 and a master valve 305 Which is the same construction as the master valvev |51 and which is a part of the motion transmitting means 228. The master valve 305 controls the pilot piston 302 in the same manner as the master valve |51 controls the pilot piston |96 that actuates the vane 31. The shaft 306 of the motion transmitting means 226 has a pinion gear 303 anchored on the end thereof and is arranged to mesh with rack teeth 304 for holding the pilot plunger |85 in a xed position when the master valve 305 is in its neutral or normal position. Fluid under pressure from the pump is admitted to the master valve 305 through a pipe ||9 and the flow of the fluid to and from the master valve 305 to the opposite side of the pilot piston 302 is caused to Dass through ducts 3|0 and 3| The construction and operation of the motion transmitting means 228 is the same as vthat previously described withy reference to the motion transmitting means 36 for governing the position of the control vane 31. The slidable and rotatable position of the plunger 3M of the master4 valve 305 is actuated by a gear. 3|6 which meshes with the rack teeth 3l1 having the ends thereof respectively connected to the pressure actuating devices M5 and M6. The pressure responsive device |45 is connected by a duct l" to the low pressure side of the venturi 260 in the feed pipe 259 from the pump 56,- and the pressure responsive device M6 is connected by a duct |48 to the /high pressure of the venturi 26m. The differential pressure between the two responsive devices M5 and Mii is a function of the quantity of liquid or fuel *nowing from the pump tit to the metering device t3. inasmuch as the motion transmitting means 22h is effective in producing a movement which corresponds to a function of the fluid ilow through the venturi 260 and inasmuch as the motion transmitting means 2id controls the position of the follower plunger itt as governed by the pilot piston Zilli, the position of the positionable plate ttl is vlilrewise governed by the fluid flowing through the venturi itil. The position of the positionable plate it?! controls the point at which the valves ttt upon the left-hand end of the valve stems itt close to begin to eject fuel from the cylinders itt. In other words, it is not until the valve sleeves ttl engage the valves 265 that 4 the fluid is entrapped in the cylinders 262 at reciprocal movement of the valve-like piston 25d'.

That is to say, it is notuntil the caps tgl are pulled' away from the positionable plate ttl that the valves tot are closed which initiates the eiec- The tion action of the valve-like pistons 26d. rotatable casing lili of the motion transmitting means itt is governed by a gear t2@ operated by the flexible shaft till from the throttle device tu. The rotation of the rotatable casing SI5 with reference to the slidable and rotatable plunger illsl provides for repositioning the' pilot plunger it which governs the location of the follower plunger i9@ that actuates the positionable plate ttl. The operation of the follower plunger it@ as controlled by the pilot plunger H35, which is supplied with iiuid through the duct 294, is the same as the operation ofthe follower plunger it@ that actuates the control vane 3l. Consequently,

, the amount of fluid ejected from the cylinders itil upon each reciprocal movement of the valvelike pistonZGl is controlled by the throttle device 3b. In addition, the differential action of the pressure responsive devices |45 and M6 maintains the volume of each ejection of the valvelike piston 26d in accordance with the amount of fluid flowing through the venturi 260. My system provides for supplying both air and liquid fuel to an internal combustion engine and of varying the ratio of thequantity of air to the quantity of liquid fuel delivered'to the engine.

Although I have described my invention with a ycertain degree of particularity, it is understood common chamber, first variable means forV regulating the now of the air throughv the air passage, second variable means for regulating the flow of the liquid through the liquid passage, the improvement of a joint regulating mechanism for operating the variable means comprising, in com.. bination, operable control means having a first means for governing the rst variable means and a second means for governing the second variable means, joint means for operating the first and second means, and variable connection means between the rst and second means to vary the ratio between the amount of air and liquid delivered to the common chamber, said variable connection means including a common control member and two rotatable members actuated by the common control member, and means for moving the two rotatable members relative to each other.

2. In a fluid control device including an air passage and a liquid passage jointly feeding a common chamber, first variable means for regulating the flow of the air through the air passage, second variable means for regulating the flow of the liquid through the liquid passage, the improvement of a joint regulating mechanism for operating the variable means comprising, in combination, operable control means having a first means for governing the rst variable means and a second means for governing the second variable means, joint means for operating the rst and second means, variable connection means between the first and second means to vary'the ratio between the amount of air and liquid delivered to the common chamber, means responsive to the air flowing through thel air passage for maintaining the iiow of air at a predetermined value, and means responsive to the liquid flowing through the liquid passage for maintaining the flow of liquid at a predetermined value.

3. In a fluid control device including an air passage and a liquid passage jointly feeding a common chamber, iirst variable means for regulating the flow of the air through the air passage, second variable means for regulating the flow of the liquid through the liquid passage, the improvement of a joint regulating mechanism for operating the variable means comprising, in combination, operable control means having a first means including a first fluid pressure device for governing the nrst variable means and a second means including a second fluid pressure device for governing the second variable means, joint means for operating the first and second means, variable connection means between the first and second means to vary the ratio between the amount of air and liquid delivered to the common'chamber, means responsive to the air flowing through the air passage to operate the first fluid pressure device for maintaining the flow of air at a predetermined value, and means responsive .to the liquid flowing through the liquid passage to operate the second fluid pressure device for maintaining the flow of liquid at a predetermined value.

4. In a fluid control device including at least a first and a second fluid feed passage, the improvement of a fluid proportioning device comprising, rst variable means for regulating the flow of the fluid through the first feed passage, second variable means for regulating the iiow of the Vfluid through the second feed passage, joint means for operating both said first and second variable means, and proportioning means for modifying the joint means to vary the ratio between the amount of fluid delivered by the first and second fluid feed passages, said proportioning means including a reciprocaliy mounted common control member and two rotatable members -actuated by the common control member, and cam means governed by the reciprocal movements'of the common control member for rotatively moving one of the rotatable members relative to the other.

5. In a. fluid control device including at least a first and a second fluid feed passage, the irnprovement of a fluid proportioning device comprising, rst variable means for regulating the now of the fluid through the firstfeed passage, second variable means for regulating-the flow of the fluid through the second feed passage, joint means for operating both said first and second variable means, proportionlng means for. modifying the lolnt means to vary the ratio between the amount of fiuid delivered by the first and second fluid feed passages, said joint means having a first movable element for transmitting movement to the first variable means and having a second movable element for transmitting movement to the second variable means, and said proportioning means having means common to both said movable elements for varying the movements of said movable elements with respect to each other.

' 6. In a fluid control device for an internal combustion engine including an air passage and a fuel passage feeding a cylinder, the improvement of a feed proportioning device comprising first variable means for regulating the ow of the air through the air passage, second variable means for regulating the flow of the fuel through the fuel passage, joint means for operating both said first and second variable means, and proportioning means for modifying the joint means t`o vary the ratio between the amount of air and fuel delivered to the cylinder, said proportioning means including a common control member and two rotatable members actuated by the common control member, and means for movingthe two lrotatable members relative t each other.

'7. In a fluid control device for van intemai' combustion engine including an air passage and a fuel passage feedinga cylinder, the improvement of a feed proportionlng device comprising first variable means for regulating the flow of the air through the air passage, second variable means for regulatingthe flow of the fuel through the fuel passage, joint means for operating both said rst and second variable means, proportioning means for modifying the joint means to vary the ratio between the amount of air and fuel delivered to theV cylinder, said joint means having a first movable element for transmitting movement to the first variable means and having a second movable element for transmitting movement to the second variable means, and said proportioning means having means common to both said movable elements for varying the movements of said movable elements with respect to each other.

a. In a nuid control device for an internal combustion engine including an air passage and a fuel passage feeding a cylinder, the improvement of afeed proportioning device comprising first variable means for regulating the flow of the air through the air passage, second variable means for regulating the flow of the fuel through the fuel passage, joint means for operating both said first and second variable means, proportioning means for modifying the joint means to vary the ratio between the lamount of air and fuel delivered to the cylinder, means responsive to the air owing through the air. passage for maintaining the flow of air at a predetermined value, and means responsive to the liquid flowing through the liquid passage for maintaining the flowl of liquid at a predetermined value.

9. In a fluid control device including at least a first and a second fluid feed passage, the improvement of a fluid proportioning device comprising, first variable means for regulating the flow of the uid through the first feed passage, second variable means for regulating the flow of the fluid through the second feed passage, joint means for operating both the said first and second variable means, proportioning means for modifying the joint means to vary the ratio between the amount of fluid delivered by the first and second fluid feed passages, means responsive to the fluid flowing through the first passage for 40 maintaining the flow of fluid at a predetermined vvalue, and means responsive to the fluid flowing the flow of the fuel through the fuel passage. I

joint means for operating both said first and second variable means, and proportioning means for modifying the joint means to vary the ratio between the amount of air and fuel delivered to the cylinder.

THOMAS A. BAKER. 

